Long stock fabricating machine



1936. J. H. ROBERTS 2,032,098

LONG STOCK FABRICATING- MACHINE Filed Feb. 12, 1931 10 Sheets-Sheet l Feb. 25,1936. J. H. ROBERTS LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1931 10 Sheets-Sheet 2 hm bHH he an mm mm ATTORNEY Feb. 25, 1936. J. H. ROBERTS LONG STOCK FABRICATING MACHINE} Filed Feb, 12, 1931 10 Sheets-Sheet 3 ep 0 er fi/fwmw TTORNEY I Feb 25, 1936. J. H. ROBERTS LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1931 10 Sheets-Sheet 4 H INVENTOR BY JosqiofllQberh.

TTORNEY Y J. H. ROBERTS 2,032,098

LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1931 10 Sheets-Sheet 5 mgllll F 25, 1936. H. ROBERTS 2,032,098

LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1951 10 Sheets-Sheet 6 a $1 $5 v INVENTOR Josewuioberts.

TTORN EY Feb. 25, 1936. J H, ROBERTS 2,032,098

LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1931 10 Sheets-Sheet 7 'k\\\\\\\\\\\\\\\\\\\ Q Q a w. n

w l Q r I J. H. ROBERTS 1 2,032,098

LONG STOCK FABRICATING MACHINE Filed Feb. 12, 1931 v 10 Sheets-Sheet 8 VINVENTOR ORNEY @{Llilioberfa Feb. 25, 1936.

J. H. ROBERTS LONG STOCK FABRICATING MACHINE QOv ENM R 3 3 l0 Sheets$heet 9 INVENTOR Josfllifloberfs. )7ATI'ORNEY Filed Feb. 12. 1951 Fab 25, 1936. J. H. ROBERTS LONG STOCK FABRICATING MACHINE Filed Reb. 12, 1931 10 Sheets-Sheet 10 INVENTQ}? b i J LRo ar s.

TTORNEY u do MW p 1-23, being for Patented Feb. 25, 1936 LONG Joseph H. Roberts, Waterbury, Conn., assignor The F. B. Shuster Company,

a corporation of Connecticut Application February 12, 1931,

which incidentally cooperate to which is frequently a coiled condition, said flying-shear to an elec vention in the accompanying drawings, Figs. flat-wire stock in the order of three thirty-seconds of an inch in thickness and of two and Referring to the Fig. 1 is a partial front elevation showing the left-hand portion the right of this figure being the left end of the discharge unit D3 the rest of the length of which is shown in Figs. 1A, 2A;

Fig. 2 is a plan of Fig. 1;

Fig. 1A is an elevation to the right of Fig. 1 illustrating the stock-discharging apparatus portion D3 of the machine;

Fig. 2A is a plan of Fig. 1A;

Fig. 3 is an enlarged end elevation partly in section on line 3-3 of Fig, 1, looking leftward from discharge-means D3 toward brake W (left),

clutch-tripping magnet 85;

Fig. 4 is an enlarged rear-elevational view from Fig. 5 is an enlarged front elevation of the brake mechanism W of Fig. 1, viewed from 55 STOCK FABRICATING MACHINE New Haven, Conn.,

Serial No. 515,199

of Figs. 2-3; and shows shear-shaft 40 and its clutch-shaft 42;

gear l8 driven from Fig. 6, showing th is a central vertical 3; and shows the heavy fly-wheel gear 5!, a

which pin 39 drives Fig. 7 is an end machine, at the right of pivoted stock-dischargin discharged cut stock e shear section U with blades G, H, on line 66 of Fig.

continuously-running large,

nd crank-arm 38 of said blades;

elevation of the assembled Fig.

1A, and shows the g member 91 and the Fig. 8 1s a fragmentary enlargement of the end elevation of Fig. 7 sh tail the end construction 0 98, pivoted discharger 97 and the target K;

on of the right owing in greater def the stock-guides 96,

r bottom guide 96,

Fig. 9 is a fragmentary enlarged front eleva- Fig. 10 is a prespective of target K of Figs. 8-9, showing its association with stock-guides 98,

98 and butt 96, and the electric switches Fig, 11 is a fragmentary tion on line i I of Fig. 7, ing for the discharge mechan of Fig. 1 and in Figs 'Fig. 12 is a tally perspectiv mechanism U, showing a target K, this Fig. of Fig. 8;

Fig. 14 is a section at I 4l 4 stock Z, the lateral om stock-discharger for target K;

vertical front elevashowing a mountism D3 at the right e of the flying-shear portion of the horizon- 13 being a. section at I3 |3 of Fig. 9 showing,

Fig. 10, other parts of the switch for magnet 85 for target K Figs. 15-15A to 18-1 views in series which illustr cams 21 in Figs. 15A- tom stock-support 95 down out stock Zl, of the helical Fig. 7 spring against s 64 of Figs. 15A-18A, Fig. 15 shows the preshearing stationary positi blades G-I-I, with t he crank 18A, which act to 8A are related skeleton move botwardly to discharge the closing action on of the shearing -pins 39 near 7: 45

7 stock-discharge cam of the crank-operated oclock of their rotation which is anti-clockwise as viewed from the front'of the machine, Fig. 1;

Fig. 15A shows the companionatenormal zero position of the stock discharge cams 21 and stock-guide box 98, 98, 96; r j r Fig. 16 shows a posthearing position of the blades G- -H with the crank-pins 39 in a different position from Fig. 15 but yet near "7:15 oclock, just after shearing;

Fig.16A shows a view showing stock-discharge cam 21 operating at the same time as Fig. 16 to open the stock discharge box 98, 96 to initiate the discharge of the sheared sub-length Zl 7 Fig. 17 shows the quick acceleration of blades G- -H to positions to right in advance of the during the time while v freshly formed stock-van, crank-pins 39 have movements principally horizontal, i. e. in the vicinity of. 6:00 oclook;

Fig. 17A for the same time as Fig. 1' 7, shows 21 fully actuated completing dumping the sheared sub-length ZI r Fig, 18 showing blade H raised clear of the oncoming stock-van as crank pins 39 are revolved upward toward 3:00 oclock on their way toward their normal position of Fig. 15, i. e., while stock Z is free from blade H to continue its uniform rate of feed to right;

And Fig. 18A, at the same time as Fig. 15A,

shows stock-discharge cam 21 at the beginning of its non-operative half-revolution of anticlockwise return to the zero stationary position of Fig. 15A;.bottom stock-support 96 having been promptly returned to stock-supporting position afterdischarge, Fig,1'7A, of'cut stock Zl;

Fig. 19 is a perspective showing of the specific form of horizontally-reciprocating die or blade G; Fig.- 20 is a general perspective showing the connections by which clutch L is tripped by the operation of magnet r r Fig. 21 is a'diagrammatic showing of the relations of various elements of the machineof Fig. 1 asa whole, from reel A at left to target trip K at right;

,Fig. 22is nism for clutch L, in its normal latched position, at vertical section 22-22 of Fig.- 3, right;

thisbeing .while the shearmgmechanism is in" its-normal stationary condition of Fig. 15;

Fig. 23 is the same as-Fig. 22' but said tripping mechanism in .itsintermittent unlatched position; -this being during the movements of the shearing mechanism in Figs. 16-18; andr Fig. 24 is a diagrammatic front-elevationalsection of a machine embodying a-modification shearing mechanism of Figs. 1-23, this machine being especially adapted for fabricating. steel strip .1-23-is designed.

-The following is an index of 'theoperations," the operator facleft to right Figs. 12, and 21,

mg the rfront-and the various controls. The

,heavy coil .or roll of very long steel strip-like stock Znfrom the-mill, anddesired to be fabricated into sub-lengths of position of reel A..

ofpower-operatedpinch-feed rolls Cl, Figs. 1,

21, by which 2 ispower-fed continuously right; longas the machine is in' operation, toithe pairs of spaced and staggered- 1-, 21, thru pinch-rollsCh" ward, Figs. 1-2, 21, .as

feed-rolls ,C, -Figs.

guidance to the shear elements fabricating unit or 7 thru the stock-guidesjof the discharging mechaan elevationof the tripping mechastock of an'order of V widths-substantially larger than the flat-wire? or narrow strips for which the machine of Figs.

uniform linear dimen sionsLis raised fromthe-fioor to the dispensing The operator then-proceeds 7 to insert the van-endthru the guideunit 13;- Figs. 172,-, and into the initial -pair,-in unit Di Figs. 1, 21, thru the guide unit Bl, Fig. 1, into the initial pair, in unit DI of power operated edge pinch-feed rolls CIV, Fig. 21, whence Z is further power-fed continuously rightward to the pairs of adjustably spaced and staggered edge feed rolls CV, Fig. 21, thru the edge pinch-rolls CIV, Fig. 21, thru the guide-unit B2, Fig. 1, into the final pair of push-pull feed-rolls CIL of unit D2 and out thru the guide-unit B3, Figs. 1, 21, to

be'received by guide-unit Bd, Fig. 6, for final .G--H of the flying shear ll, and beyond nism D3, Figs. 1, 2, 15A, 18A, until the van of Z operates the length-master tripping unit K, Fig. 21, to initiate the. functioning of clutch L, Fig. 2, (i. e., to unlatch it from Fig. 22 to Fig. 23), to operate blades G -i-l of the shearing mechanism U thru their cycle, Figs. 15-18, of severing a subtreated advance-portion of length from off the the parent stock Z and returning to normal stationary condition ofFig. 15; the fresh vans of the parent stock Z so created being continuously fed forward thru the path of their predecessors Zl to make contact with and to operate the length-master tripping unit K, for pro-gauging thelinear dimension of the cut sub-lengths Zl.

V Stock-guides V The successive H guiding-stock Z, 'leit to right Fig. 1 from reel A thru tothe-fabricatingunit U and beyond, are severally constructed and function as follows:

The guide-unit B is of special transverse swivel design whereby :thestock stock guide units 13-34 for Z in its entrance from reelA to the stock-treatingunit D may be guided I to 'pass longitudinally central and/or parallel between the roll-stand members Illa-i2 5 of unit D,- g. i

The guide-unit B is supported by the bracket ceive thedownward extending vertical swivel- '40 casting l'29; left-Fig. l; which is formedto re-- stem 1190f the swivel'guide-plate E13; said swivelstem H9 being fitted with a manually controlled lock-I89, Figz'l, while atits lower extremity there is fitted'a worm-gear i8 I'which intermes'nes with a manually operated worm !82' mounted in I29,

' Fig; 'l; which 'allowsthe' operator to minutely align the direction of Zs entrancethru said unit D;

:The swivel-plate by 119 in 129 is fitted with "the top and bottom guide rolls l83-l34, a surface wearing strip 266 of hardsawn-brass, and at least' one pair of edge.

guide-rolls 231, Fig. 2, the latter beingcapabie of adjustment towards oraway from each other to'ac'commo'datethe variations ofwi'dths of dif ferent coils of stock Z which may be selected for treatment in'the exemplary machine. h

f'fiie 'guide unit' Bl, Fig. 1, pi: forms to guide stock' Z,'as it emerges from the last pair of rolls CI of unit D, beyond to the first pair of rolls CIV of the vertically guide 'BI having itsilower components supported fr'ombelowby'the bracket .132, Fig. 1,. to which a'surface wearing plate 293. 1 l

' The upper components of unit Bl are supported fromabove off 'the roll-stand frames" i25-i23 by the overhanging ensemble of supporting elements 204 from whichsupporting-elements is ad-' justably suspended the top-guide or pre'ssor-foot 295, Fig. 1 which insuresthe entrance of stock? to the'more' or less grooved tical'unit'Dl', Figs. I-Z;

513 of guide-unit pivoted V disposed unit Dl', Figs. l 2; said e l lll' i e vet:

05' V are adjustably fixed the edge guide-rolls 292 and A The construction of the stock-guide unit 132 is analogous to that of BI altho it is not necessarily equipped with the equivalent of B Is edge guiderolls 202. The function of this guide-unit is to receive stock Z as it emerges from the last pair of rolls CIV of vertical unit DI and to conduct the same tothe push-pull pinch-feed rolls CIL of unit D2, Fig. 1, which feed stock Z into the guidance of unit B3.

Guide unit B3 is constructed mainly of an upper guide element 201 and a like lower guide 208, Figs. 1, 2, 6, each of which guide-elements 20'I2D8 terminates in a narrow rightward extension which cooperative form a birdbill-like guide-structure thru which the continuously moving stock Z is guided to bridge the intervening gap from the rolls CIL rightward to the hollow-die or lower blade G, Fig. 6; all this while the guide-unit B4, which is dually fixed to the blade carrier F, assists in a telescopic manner to interslidingly support the rightward projecting ends of the guide-elements 201-408 of B3, Fig. 6.

The rightward extensions of the guide-elements 2Il'I-203 of unit 133 are preferably formed narrow to accommodate the processing of the narrower widths of stock Z which may be as narrow as onehalf inch more or less (fiat-wire) so that the cooperating edge-guides 2|!) of unit B4 may be transversely adjusted to adjacent positions at each side of the said narrow rightward extensions of the guide-elements 201-208 to insure that the narrow strips of stock Z will safely enter the orifice of the hollow-die or lower blade G, Fig. 6; said cooperating edge-guides 2I0 being preferably fixed to the cover member 220 of guide unit 134 by the cap-screws 2I3A, Figs. -6.

Power All of the foregoing cooperating stock-treating units assisted by the stock guides B-B4 operate in tune to treat and feed the stock Z to and thru the flying-shear elements of unit U and to subsequently produce sub-portions ZI of uniform linear dimension; and all but reel A are driven by a common driving means such as electric motor P, Fig. 1, by way of a series of inter-connected driving shafts (i. e. the worm-shafts I53-I53A I53B of the commercial reduction-units I2I, I24 and I24V) all of which are arranged parallel with the line of stock-feed and extend longitudinally of the machine. Reel A may or may not be power-operated, as below.

The motor P is positioned on that depressed portion QI, Fig. 2, of the bed-plate Q partially lying within the general supporting structure of the machine, and is power-connected with the worm-shafts I53--I53B via a multi-strand V-belt drive R, Figs. 1-2, 4 and the inter-connecting flexible couplings I4-I4A, Fig. 1; said wormshaft I53A having an additional outboard bearing support I54, Fig. 1, on its long extended portion adjacently positioned to the flexible coupling I IA, Fig. 1.

The power received from motor P is transferred from the driving worm-shafts I53I53B, Fig. 1, to the several operating components as follows:-

(1) From the worm-shaft I53 to the ensemble of rolls C-CI, which are grouped in the preliminary stock treating unit D (upper left. Figs. 1, 21), the power drive is suitably reduced in revolutions per minute by the worm I89 and the worm-gear I90 of the commercial worm-gear speed reduction unit I24 driving rolls C-CI at an optimum rate of stock feed; said worm I89 being mounted on high-speed shaft I53 and worm-gear I90 on the low-speed shaft TI; both I89-I 90 being supported within the general housing of the unit I24 and shaft Tl being extended transversely rearward of the reduction unit I24, Fig. 1, to drive via spur gears 44, 65 and 45, Fig. 1, the gear-box ensemble 1, top left, Fig. 2, which distributes rotative power via universal joints I53 to the rolls C-CI of unit D; said worm-shaft I53 being connected with and driven from the wormshaft I53B by the flexible coupling I4, Fig. 1;

(2) From the worm-shaft I53B to the ensemble of rolls CV-CIV, which are adjustably grouped in the secondary stock treating unit DI (top center, Fig. 1) the power drive is suitably reduced in revolutions per minute, by the worm I89V and the worm-gear ISOV (not shown) of the commercial worm-gear reduction unit I24V, driving rolls CV-CIV at an optimum rate of stock feed; said worm IBSV being mounted on high-speed shaft I53B; and worm-gear I9I3V (not shown) on the low speed shaft T2; both I89V-I9IJV being supported within the general housing of the unit I24V and shaft T2 being extended vertically downwards of the reduction unit I24V, Fig. 1, into the gear-box ensemble V which distributes power to drive, via the spur-gears I0, II, I2 and the intermeshing idler gears I3 (not shown), Fig. 1, the superimposed adjustable stock-treating unit ensemble DI; this thru the universal joints I59V which are connected to the spindles of the rolls CV-CIV of said unit DI; said worm-shaft I53B being connected with and driven by the wormshaft I53A thru the flexible coupling I4A, Fig. l; and

(3) From the worm-shaft I53A to the ensemble of the pull-push pinch-feed rolls CIL of the third stock treating unit D2 and to the flywheel bullgear 5I of clutch L for intermittently operating the flying-shear components of unit U (right Fig. 1), the power drive is suitably reduced in revolutions per minute, by the worm I22 and the wormgear I23 of the commercial worm-gear speedreduction unit I2I, bottom right Fig. 1, driving rolls C IL (and incidentally fly-wheel bull-gear 5 I) at tuned rates corresponding to the associated stock-treating units D-DI; said worm I22 being mounted on high speed shaft I53A; and wormgear I23 on the slow-speed shaft T; both I22-423 being supported within the general housing of the unit I2I and shaft T being extended transversely rearward of the reduction unit I2 I, Fig. 1, to support and drive from the pinion gear 50, Figs. 1, 3, 4, and 20, to the gear-box ensemble J, central right Fig. 2, and the fly-wheel bull-gear 5| of clutch L which incidentally and normally acts only as an idler gear between pinion-gear 50 and the gear 49 mounted on spindle IB'IA, Fig. 2, of unit J which unit distributes rotative power via universal joints I5I3A to the rolls CIL of unit D2; said worm shaft I53A being connected with motor P by the multistrand Vbelt drive B, Fig. 1.

Speeds which ranges from 533 to 1600 R. P. M.; said inter-connected Worm-shafts indirectly driving 'all the various component units of the machine at substantially reduced revolutions per minute, 5 as follows:

The reduction ratio, Fig. 1, between the two worms I89-|8V and their respective worm-gears I90-I9BV, all of which are supported within the oil-tight casings of the two reduction units l24-l24V, is as 1 is to 4 and shafts TI and T2 for respectively driving rolls C- -CI of unit D and rolls CV-C IV of unit DI will thereby be theoretically rotated (according to the adjusted speed of mote-r P) from 110% to 331 R. P. M.; this speed 5 of shafts Tl-T2 is incidentally the same as that of the spindles of rolls CCi and CVC IV so that the connecting trains of gearing 44-46 and Ill-II between said shafts Tl-T2 and the power distributing units I, V are of a oneto one ratio. r V

Likewise, the reduction ratio, Fig. 1, between the worm 122 and the worm-gear I23 supported within the oil-tight casing of the reduction unit 12! is as 1 is to 3 and shaft-T, for driving the rolls CIL of unit D2, is thereby theoretically rotated (according to the adjusted speed of motor P) from 147 to 441% R. P. M.

' The differences in the reduction ratio of the above reduction unit I2 I, contra the before mentioned units |24l2lV, is primarily because shaft T mustrotate at a sufficiently high rate of speed to drive the combination pseudo-idler flywheel bullgear 5| of clutch L with at least a 1 to 3.2 reduction ratio in the exemplary machine so that said flywheel clutch-member has a rate of rotation foot- -(according to the adjusted speed of motor P) in the order of from 46 to 138 R. P. M.; therefore there is incidentally and necessarily a further speed reduction of as 7 is to 10 between the driving pinion mounted on the rearw'ardly extending slow-speed shaft T of the reduction unit I2! and the power-receiving gear 49 of the unit J which distributes power to rolls CIL via the universal joints I50A, Fig. 2; all this to maintain the several eifected components in'tune .with the 45 rest of the machine. Thus is seen that stock Z is continuously'unreeled from A and fed left to right, Figs. 1, 21, for

treatment in the roll ensembles D, DI, and D2 continuing on thru the flying shear unit U of the -rnachine and beyond into the stock-guides 96, 98,

until the van of Z pre-gauges the linear dimension of a fabricated sub-length Zi and causes the shearing thereof from the parent stock Z when contact by the van of Z is made with the: targettripping unit K, Figs. 1A, 9, 21.

Stock-reel The stock-reel A is preferably but need not be of a power-operated'type as set forth in my prior application for patent Serial No. 437,305, filed 20 March, 1930, wherein the turntable of the reel,

which in the excl plary machine supports the stock coils of Z-preferably in'the manner shown on a horizontal axis, see Figs. l-2, 21, is power raised and lowered from the floor by the operators control of the stock-reel motor. a a

Feed-s CIL of unit D2, Fig. 21.

and feed stock Z' at the same rate, which in th feet per minute. V

Dis-assembly plary stock-treating machine.

General dimensions thirty-eight inches from the floor-level. The rc-lls C, Cl, ClL, CV, and CW have normal work-engaging diameters of two and 'five-eighths inches.

7 The stock-receiving and discharging apparatus (partially shown at the right of Figs. 1-2 extended to include Figs. 1A-2A) has a capacity for handling sub-lengths Z I of stock Z from three up to and including twenty feet long; and this may be varied in construction to have a greater or less length capacity as may be desired by the designer.

The stock shearing unit-U has. an extreme reciprocatory movement of nine inches which may also be re-pro-portioned by the designer according to the principles for cutting continuous feed stock at high rates as set'forth in prior application Mounting of shearing mechanism The shearing mechanism U, Figs. 1, 3-6, 12, 15-18 for fabricating continuously fed stock, also constructed as a'detachable-unit, is mainly built up and supported by the steel frame casting .36. Figs. 1,. 2, 3-6. which is mounted on the table; support member M4 at upper right in Fig. 1,; and only the one-revolution clutch shaft 42, Figs. 2, g, 3-6, requiring additional support, as by the bearingsupport member 215, Figs. 2, 3, which is fixed,

Shearing mechanism U 42 are normally at rest, being so held under-the As to proportions, the exemplary machine'as depicted in 1-2A is shown at a reduced scale of substantially three-quarters of an inch to one The work-line of stock-feed is shown as for patent, Serial No. 403,716 filed 31 October, 1929.

stantly rotated pinch-feed rolls Cl feeding Z forward to thru the several stock treating elements D, D2 to the p'ull-push pinch-feed rolls Feed rolls C-C|, CV-CIV rotating on their several arbors, as well as rolls CIL, are all power operated between the speed-range of 110 and 331 R. P. M. and all these rolls incidentally treat exemplary machine is in the order of 75 to 225 1| The general design and construction of the exemplary machineis suchthat any or all of the various reduction units, gear-boxes and stock treating units, including the flying-shear unit U of themachine and the stool; receiving and discharging apparatus can be conveniently separated or stripped 01? from the stationary skeleton of the machine (by such an expedient as the re-. moval of the attaching bolts and dowels) for'removal therefrom for repairs or alterations whens such become necessary, said detached units being then transportable to the machine-shop which 5 in a modern steel plant may be located a mile distant from the operating location of the exemtothe top of the end-pedestal 432, Fig. 3, adja- The shear-shaft 40, 4|, Fig. 12, and clutch shaft influence of the brake mechanism W, Figs. 1, 2, 3, 5, while the flywheel bull-gear of clutch L. Figs. 2, 3, 4, 5, is rotated idly on clutch-shaft 42 by motor P without connection to said shaft, until the van of the parent stock Z, acting thru the target-switch unit K, Fig. 10, causes the coils of the solenoid electromagnet 85 to be energized for tripping the clutch L with the resultant locking of the clutch to shaft 42 for a single rotation which, Fig. 12, thru the gears l'l-l8, l8A of equal diameters, causes the short shafts 404l and their crank-arms 33 to make one revolution, causing one revolution of crank-pins or trunnions 39, and a single cycle of the flying shear elements F, G, 34, and H, to shear a sub-length Zl from off the continuously fed parent stock Z; element F carrying blade G, Fig. 15, element 34 carrying blade H, and the horizontal component of the revolution of element 34, by interconnection with carrier F, causing horizontal reciprocation of the cutter and its blade G; and said operation by short shafts '49-4l of said shear elements being effected thru the crank-arm members 38-38 which are transversely bored and fitted with hardened steel bushings 43 near their ends to receive the pins or trunnions 39 of bronze bladecarrier 34; this transverse boring of the crankarms 38 in the exemplary machine having an eccentricity (or throw) of four and one-half inches from the centers of shafts 40, 4|, imparting a nine inch throw to the elements F, G, H and 34, the speed of operation of the machine being determined and controlled by the length of such throw. Thus carrier 34 for blade H is revolved but not rotated by crank-arms 38, and carrier 34 in said revolution and its reciprocation of carrier F for blade G, reciprocates up and down between the adjacent guide-faces of F. In Fig. 12 the G-carrier F is broken away to show clearly the H-carrier 34 and trunnion pins or crank pins 39; F being shown complete in Figs, 6, 15-18 including two uprights F, F spaced apart fore and aft in the direction of stock-feed and held by top-piece Fl, the horizontal space between F, F, being filled fore and aft by H-carrier 34 which slides up and down beneath top Fl along the facing inner vertical surfaces of said uprights F. Thus Figs. 12, 15-18, as pins 39 (loosely connected to either 38 or 34 as desired) are revolved by arms 38 in a fore and aft circle along the line of stockfeed, anticlockwise (when 34 normally lies above the work-line or line of stock-feed) the horizontal components of the motions of pins 39 cause them to exert a push-pull effect on G-carrier F (on uprights F, F) to reciprocate said carrier horizontally; and the vertical components of the revolution of 39 are permitted by the freedom of H- carrier 34 for its up and down reciprocation between the uprights of G-carrier F below top Fl. An important advantage of the above crank-armand-pin shear-operating mechanism is its. inherent light-weight construction which is important as one of the features which make practicable the hereinafter described accurate production operations of the machine. While crank-pins 39 may be operated from shafts 45, 4|, Fig. 12, by way of any suitable crank-wheels or crank-disks on said shafts, including mounting of pins 39 on gears l8, lBA or on 'crank-arms 38 in the form of disks, yet preferably pins 39 are mounted on parts other than gears l8, SA, and for the purpose of providing a lighter construction in which the crank-arm-and-pin construction is inherently capable of embodiment, the crank-arms 38 instead of being coupled disks may be in the form of single radial arms extending from the short crank-shafts and having no more mass than is desirable to withstand the shearing stresses.

Fig. 15 shows the normal conditions of rest as determined by clutch L, by the connections therefrom to pins 39, Fig. 12, and by brake drum Bl, Fig. 12 of brake W, Fig. 5; crank-pin 39, Fig. 15, being at about 8 oclock (hour-hand criterion) of the anti-clockwise rotation of its crank-wheel 38 (or preferably as near to 8 and as far from 12 oclock as practicable) pins 39 holding blade H only slightly above the horizontal stock-passage thru channeled blade G, Fig. 19, in readiness for prompt shearing cooperation between tools H and G by rotation of crank-wheel 38 forthwith upon commencement of downward movement of H caused by the abutting of the advanced right van of stock Z, Fig. 10, against target K, Fig. 21, operating the electromagnet 85 and the connections, Fig. 20, to clutch L, to unlatch said clutch from the locked condition of Fig. 22 to the shear-operating condition of Fig. 23, and connect constantly running fly-wheel gear 5!, Fig. 3, to clutch-shaft 42, Fig. 12, and impart a single rotation to shafts 49, M, gears l8, I9A and crank-wheels 38, a single revolution to crank-pins 39 and H-carrier 34, and a single complete reciprocation to G-carrier F,-brake W, Fig. 5, with its drum 6|, Fig. 12, assisting the inertia of the parts in stopping them in their normal positions of rest in Fig. 15.

In preferred construction and operation, the revolvable tool H first moves toward stockv Z, Figs. 15-16, immediately effecting shearing after starting from its normal position of rest, then it moves upwardly, from 6 to 12 oclock anti-clockwise, and finally completes its single revolution by moving downward from 12 oclock. During all of this revolution of tool H after shearing, the stock-feed continues, but there is but little stockfeed before shearing after the start of the revolution of the tool.

Of such complete cycle, Fig. 16, contrasted with the normal stationary conditions of Fig. 15, shows the positions of the parts after the short anticlockwise arc of movement of pins 39 from about 8 oclock, Fig. 15, thru the commencement of shearing at about 7:35 oclock (hour hand of clock) to just beyond the completion of shearing at about 7:25 oclock; the sheared sub-length Zl as a whole, Fig. 16, having been started at the proper time after completion of shearing, in its discharging movement from its position causing desired continuation of operation of shearclutch as L, the discharger in the example here being by quantity, Fig. 16A, consequent upon the depression of guide-bottom 96 by cams 21. In this clock analogy, each clock-dial minute over which tool H moves is an arc of six degrees, and five minutes of the clock-dial is an arc of thirty degrees; so that the above specified arc of actual shearing movement of revolving blade H (like a clock hour-hand) from about 7:35 to 7:25, being one sixth of the five-minute clock-dial, is thru an arc of five degrees, in the machine in the form designed for shearing narrow strips, the circle of revolution of tool H having a diameter of about four and one-half inches as described above, and the vertical movement of tool H during its five degree shearing arc of its revolution being about three-tenths inch or a little less.

The van length of stock as a whole is held in its position in the line of stock-feed as long as is desirable for providing by it for the operaintended to feed stock lower transverse .at all times, since ,nected carriers) are toward 8 oclock as is tion of the clutch L, and while such van length may or may not be so held for a substantial time interval after completion of shearing, it is so'held at least up to the completion. of shearing, altho in the machine and roll-locking clutch L disclosed, the sheared stock-van is discharged relatively instantly upon the completion of shearing so that clutch L is released from control by the stock before the blades have been returned to their normal positions of rest. The five degree shearing are from 7:35 anti-clockwise to 7:25 (hourhand) centralized at 7:30, is that of the progressive action of blade H transversely across the width of the strip stock, blade H being inclined for that purpose at a raking angle transversely, the shearing beginning at the end of raked'blade H and continuing progressively across strip stock Z until the higher transverse end of blade H has completed 20 w degrees of revolution of crank-pins 39 from 7:35

the shearing. This shearing-arc of about five to 7:25 oclock is the time when the horizontal and vertical components of the revolution of said pins are such that the rate of rightward motions of blades G, H (which rates are alike the blades have interconsubstantially the same as the rate of rightward feed of stock Z by the feed-rolls, so that during the act of shearing the stock the latter is kept free from resistance to its intended uniform rate by means of the feeding mechanisms D, Di, D2, of Fig. 21. Further comparing Figs. 15-16, there is a desirably short are of motion of blade H between its positions of rest and shearing, and as shown and preferred, the normal rest position of H is in the path of its motion directly toward the stock; and preferably there is minimum downward motion of blade H between the time it starts to move from rest in Fig. 15, (preferably as low down practical), and the time G and H have sheared, just prior to Fig. 16; the important advantage of tripping of clutch L to start H from rest in Fig; 15, and the shearing, being that it eliminates all possibility of substantial departures from uniformity of linear dimensions of sublengths ZI which might result if slippage should occur between stock Z andfeed-rolls D, DI, D3 during a relatively long interval of time between initiation of movement of blade H and the shearing cooperation of G and H. While said feeding means itself operates at a uniform rate and is Z at a uniform rate, yet it has been found to be impracticable to insure continuous uniformity of feed-rateby the pinchrolls because at best the engagement'between' the stock and such feed-rolls is one of friction, and the stock is heavy, its rate of feed is desirably rapid, and at times the uniformity of stock-feed rate may be more or less interrupted. In the combination of the machine, however, the sub-lengths Zl will be substantially equal even if at any time there may be unintended variations of stock-feed rate by slippage between stock Z and feeds D, Di, D2, because, clutch L, not being tripped nor blades G or H started from, theirv positions of rest in Fig. 1 5, until the van of Z strikes target X, thereupon the shearing is effected substantially instantly (between Figs.

" 15 and 15) before any possible feed-slippage can this short time between I towardB o'clock as is practicable, that upon the tripping of clutch L, blade H requires movement over only about twelve and one-half degrees of to 7:35) before blade H engages with stock Z; and during the extremely short time of that iovementof H from 8 oclock or thereabout before commencement of shearing at 7 :35 it is impossible for feed-slippage to occur to an extent sumcient to affect materially the length of cut stock; and as soon as blade H commences to pass down across the stock-passage thru blade G, the crank-wheel 38 via the start of blade H pin 39hr as low down are (anti-clockwise from 8 to shear stock Z, positively prevents reduction of feed-rate of Z. But during the twelve and onehalf degrees of arc of premilinary movement of blades G, H from 8 oclock prior to contact of H with Z at 7:35,

of downward movement of blade Hare sufiicient,

rate of stock-feed, for

and sufficiently like the proper shearing; and furthermore, as soon as tool H has started to shear the stock it oooper ates with the feeding means in forcing the stock to move lengthwise. During the short five desaid blades have ample time for their rate to be accelerated to the rate of' gree shearing arc, 7:35 to 7:25, the horizontal rates of G and H are substantially the sameas that of Z; and there is substantial equality of both the horizontal and vertical rates of revolving blade H. By all the above, insurance thus is provided against shearing of too short sublengths Zl due to shearing action delayed after starting of the clutch so-long as to permit reduction or intermission of stock-feeding prior to shearing and after starting of shearing tools from rest. On the other hand the stopping and holding of the light-weight, intermittently operated shearing mechanism in positions of Fig. 15, by means of braking mechaprevent the possibility of the above stock-feedblocking by tool H which might occur otherwise and if the masses of the shear-operatingmechanism were large enough to cause such'high momentum as to cause the tool H, etc., to creep, in successive cycles gradually and cumulatively, beyond the desired positions of rest close to the shearing positions, so 'that eventually tool H might be broughtto rest by brake Win a position of rest corresponding to the position of initial shearing or even in front of the stock in case of such temporary discontinuance of stockfeed as might permit such movement of tool H into the stock-path. And While it is desirable, as above, to have the position of rest as close to the shearing positions as is practicable, yet itis its normally stationary V nism W (in cooperationwith the single-revolution .right at least equally desirable to have the normal ,position of rest far enough from the shearing positions to allow for the desired acceleration of tool-movement after being first moved from positions of rest. In Fig. 16, when the shearing has been completed by the movement of pin 39 anticlockwise beyond 7:25, the rate of acceleration ,of' the horizontal movements of G and H begins ;to increase very rapidly, so that as soon as shearing has been completed, Fig. 16, the rightward rate of G and H begins to be higher than that of the feed of Z, so that the van of Z, even if continuing to progress at full rate uniformly rightward, and not slipping in D, Dl or D2, lags behind G and H; so that by the time the rightward movement of G and H begins to decelerate, Fig. 17', i. e., when pin 39 begins to pass rightward from 6 oclock, the stock-van is safely behind blade H, to left, Fig. 17, and does not catch up to the right end of blade G until such rightward movement of 39 beyond 6 oclock has raised blade H up out'of the horizontal path of stock Z, which is when 39 has moved up almost to 4 oclock, and

when 39 has reached 4 oclock, blade H will be at the same height as in Fig. 15, altho thereafter, Fig. 18, H will continue upward movement after Z has caught up with and emerged from the open end of blade G, the upward movement of H continuing until pin 39 has reached 12 o'clock. While the feed of Z continues and clutch L remains unlatched, Fig. 23, L continues to cause the anti-clockwise rotation of crank-wheel 38, from 12 oclock, Fig. 18, thereby reversing the direction of horizontal movement of G-carrier F causing blade G to slide along its ways backward along stock Z until both G and H are stopped by the unlocking of clutch L, Fig. 22 at mid-rotation of the clutch, and by the action of brake W on shaft 42, in the normal positions of rest in Fig. 15 where as before they are ready for substantially instant shearing action upon the next unlatching of the clutch trip mechanism caused by the fresh van of stock Z striking target K. And throughout the time when crank-pin 39 is being given one revolution from Fig. 15, thru Figs. 16-18 back to Fig. 15, stock Z continues its rightward feed toward target K, desirably and intentionally at a uniform rate continuously; but even if that rate vary, either accidentally or intentionally, the stock Z will be sheared into equal lengths for the following reasons, owing to the cooperation between the target K, and the arrangement of crank-pins 39, and preferably the eleotromagnet linked between the target and the clutch. First, the sub-length control by target K insures that the shearing tools shall not act until the portion of stock Z which actually has been fed (even if the feed-rolls have slipped on the stock), is equal at least to the length intended and in accord with the adjusted setting of the target relative to the scale 99A, Fig. 10. But such setting of target K in any case must be relative to the time between the instant when the stock strikes the target and the instant when thereafter tool H starts to shear. Assuming a desirably rapid stock feed rate of 200 feet per minute, a substantial length of stock is required to be fed continuously at a uniform rate by the feed rolls, during the time between such instants, in order to obtain the desired sub-length for a given setting of the target; and even if less than such given length of stock be fed during the time after target operation, the shearing tools will operate pursuant to the tripping of clutch L by the target, and a sublength Zl will be produced which is shorter than that intended by the target adjustment. Thus, altho a target control of the clutch tripping insures that the clutch shall not be tripped at an arbitrary time independent of the length of stock actually fed, nevertheless the mere provision of a target does not of itself prevent substantial variations of sub-lengths Z owing to possible irregularities of stock-feed after target-starting by the van of the stock. The present invention provides for uniform lengths Zl even if there be slippage between stock and feedrolls after the van of the stock Z strikes target K, this being done by substantially eliminating the time interval between such striking and the instant when the low end of raked blade H has started shearing at one edge of strip Z; for as soon as the latter is started, inclined blade H in its action of shearing progressively across strip Z will feed the latter along with the blades G and H until shearing is completed, thereby overcoming any tendency to slippage between the stock and its feed-rolls. Part of the time between target-starting and shearing-starting (i. e., the time between target-starting and clutchtripping and starting) is eliminated by the provision of the above target-controlled electromagnetic means for mechanically tripping clutch L, this gaining time by eliminating mechanical linkage between target and clutch which otherwise would be needed and which would consume a longer time for their operation to trip the clutch. For this reason the magnet or the like preferably is employed; but whether or not it be employed, or any equivalent means for reducing the time between target-starting and clutch-starting, the remaining time, i. e. between clutchstarting and actual shear-starting is desirably substantially reduced by means of the above arrangement, including flywheel gear 5|, whereby the shear-blades are most rapidly accelerated from a position of rest so near to their actual shearing positions that there is substantially no time for either stock-feed or stock-slippage relative to the feed-rolls, the actual shearing occurring substantially instantly upon target-starting, particularly when as preferred, the time between target-starting and clutch-tripping is substantially eliminated by the provision of the electromagnetic clutch-tripper or an equivalent. As

in the arrangement of Figs. 6, 12, 15, etc., it is preferable that the normal positions of rest of crank-pins 39 and tool H shall be such that their initial movements shall be in the same vertical direction as their movements during actual shearing, i. e., that said normal positions shall be between 12 and 6 oclock of the anti-clockwise rotation; and it is preferable that such positions shall be as far from 12 oclock toward the shearing positions as is practicable in consideration particularly of the matter of acceleration by flywheel 5l of tool H so that the latter at the time of shearing shall have its full rate which is designed to be the same rate horizontally at the time of shearing as the rate of feed of the stock.

The above references to clockwise rotations are on the basis of the location of the shear-parts above the work line as is preferred. If, however, the shear parts be located below the work-line, so that blade H has its shearing movement opposed to gravity, then the rotations of crankwheels 38 will be clockwise, and the above references to 8 oclock, 7:35 and 7 :25 will be 10 oclock, 10:25 and 10:35, etc. In any case the above figures are exemplary only, altho theoretically optimum, and it is permissible not only to have quarter-cycle altho the positions of mounted at I 7 I? on shaft 42 shaft 42 'H and shearing thereby, etc.)

longer times between blade-starting and shearing but to; have shearing centered at other ablyiin the middle of said quarter cycle; and preferably the positions; of rest are in the same test usefully may be in the same half-cycle of movement of 39 and H toward the stock wherein teol H starts from rest and completes shearing all in a single short sweep toward the stock, the use of such arrangement depending on a nottce high rate of stock-feed and the degree of uniformity'of sheared sub-lengths desired. 7

Various mechanisms can be employed for increasing the rate of tool I-I so as toobtain the valuable desideratumz of as high a rate of stockfeed as is otherwise practicable. In the first place the throw or eccentricity of. crank-pins 39 can be increased so as to provide a greater rate for tool H without increasing the rate of 42. (With :clutchesa of the roll-locking type shown, a very high rate of rotation is undesirable.) r?

'Another design involves pairs of intermeshing gears lll8 and l7|8A,'Fig. 12, in the form of elliptic gears? i. e., having a pitch-line of elliptical shape. Ihese two gears of each pair areof equal size, and each has its rotation center either at a'focus of the pitch-line ellipse as commonly Withielliptic gears or otherwise in this particuiar employment of elliptic gears, at the designer. With two of such elliptic gears which drives crankpins 39, Fig. 12, and two more such elliptic gears l8, |8A on driven shafts 40, M, said driven shafts have imparted to them a higher rate eluring the quarter-cycle of shearing, Figs. 15-15, so that the rate of stock-feed can be increased accordingly or the normal positions of rest can be made closer to the positions of shearing, or the R. P. M. of shaft 62 can be reduced, or all such rates so modified, particularly if also the throw of crankpins 39, and the rate of clutch L and shaft 42 be increased to optimum. Theiprovision of these elliptical gears is of special value here, because there are practical limits to the rate of clutchso as not tocause too severe duty on clutch L in its many successive operations of locking and unlockingfone for each sheared sublength of stock; and the provision of the elliptic gears permits all the above advantages (higher between starting of tool concurrently With desirably low rate stock-feed and short are the further advantage of a of clutch-shaft 42.

A specific construction of such elliptic gearing for the machine hereof is as follows, a pair of duplicate intermeshing elliptic gears being located at |7'l8, Fig. 12, and a like pair of duplicate intermeshing' elliptic gears at Ill8A, in lieu of 12-inch circular gears, nothing else in' the ma;- chine being changed save to increase theuniform rate of operation of the feed-rolls so as to feed the stock continuously as fast as the increased rate of tools C+H at the instant of shearing,

' thereby increasing the productivity of the machine, in this instance by forty per cent. With shafts 42, 40, 4| as before, i. e5; with centers 12 inches apart for the 12-inch circular gears, Fig. 12; the elliptic pitch-line of each of the like elliptical clutch-shaft will of the blade-carrier 34 with yet it is permissible to blade-carrier 34. Also disks .38.

gears to be mounted thereon is given a longer diameter of 12 inches and a shorter diameter of about 9 13/16 inches. Alsoeach elliptic gear is bored forits shaft at a center which is offset one inch from the middle diameter of the pitch-line, that'is, the center of the shaft-opening is distant five inches from one end of the longer diameter and seven inches from the other end of the long diameter. And two of such elliptic gears are f xed to the driving and driven shafts so that the gears intermesh; for example, when the longer axis of the two elliptic gears are in alinement, the center of 'stock-feeda rate for circular gears will be 225 f. p. m., but 316 f. p. m. with the 'ellipticgears, i. e., again: an increase of about forty per cent. Thus, while the cost of making elliptic gears is high, yet they are well worth While in this in.- vention. r

A primary reason pins 39 may be close whythe normal positions of to the middle of the quarter of the longer or 12-inch one shaft will be 5 inches from the ineeting pitch-lines of cycle of revolution at which shearing is done is that in that location the rate of tool H is increasing rapidly no matter what may be its rate of circular travel; and such increase of horizontal rate is cumulative withathe accelera tion of circular rate consequent upon the tripping of clutch L. In these circumstances the provision of the elliptical gears is useful as a third cause of rapid acceleration of tool H; and this has the useful efiect, not only of permitting a higher rate of stock-feed without increasing the rate of clutch L and its shaft 42, but in permitting the position of rest of tool H to be closer to its shearing position by causing it tobe so rapidly accelerated that by the time it contacts with the stock it has attained the same horizontal rate as thatof the stock, the ultimate useful efiect being the substantial eliminationiof time between the starting of clutchshaft 42 and the starting of actual shearing, thereby preventing during such time any substantial stock-slipping relation to the feed-rolls which 7 would cause lack of uniform sheared sub-lengths.

as is shown, carrier 34 and tool H normally are at one side of the line of stock-feed, i. e., when they are in their stationary positions, Fig. '15and for that reason it is unnecessary for the carrier to be large enough to be formed witha passage; for the ffeeding stock; this being another reason for the advantage of simplicity of the machine hereof.

While it preferable to provide; the ,bronze trunnions 39 fixed to it, the

of horizontal travel relative motions being then between 39 and 38,

A have said trunnions or crank-pins 39 secured to the crank disks' 38 and journaled in suitably bushedholes formed in the may be consolidated with their respective gears I 8, I8A so as to constitute crank-wheels with toothed peripheries and with laterally projecting crankpins 39.

Shafts 40-4! which are journaled in the frame 36 are removable therefrom thru the medium of the removable bearing-caps 35-45, Figs. 3, 5-6,

which caps are held in place by the cap-screws 33, Fig. 3.

The gears H, H, is, EBA may be considered to be diagrammatic showings of any suitable gearing such as the elliptical gears hereinafter described.

When clutch L is tripped by the van of the stock, the clutch is locked to clutch shaft 42, Fig. 12, for one complete revolution; and thru the gearing i?-l3, iBA the shafts 99-4! with their crank-disks 39-58 likewise are locked to clutch L and so turned thru a single rotation as to cause the above actuation of the blade carriers 39, F by crank-pins 39.

Shearing tools The vertically reciprocating guillotine-like blade H, Figs. 6, 19, is of rectangular construction and is located between the fore and aft upright portions of G-carrier F, Fig. 6, with its presented cutting-edge positioned flush vertically with the left face, Fig. 6, of its own carrier 34; blade H being secured to 34 by bolt E, and the receivingrecess for flush blade H in carrier 34 is formed transversely angular, so as to position the cutting edge of blade H at a slight rake or shearing angle with the horizontal cross-section of stock Z (especially when a strip or sheet) and with the cutting-edge of the box-like die-ensemble G. That is, one end of blade H is a little higher than the other, so that the shearing action is progressive from one end to the other of blade H. The simple rectangular formation of blade H makes possible the use of all four of its long edges at different times for shearing without regrinding.

The blade G assembly, Figs. 6, 19, is of openended box-like formation and is retained in its carrier F by the specially formed collar-head screws 222, Fig. 6; and G is preferably constructed, Fig. 19, with top and bottom halves 223, 224; the general parting-line 225 of which is preferably at either the top or bottom (contra a mid-position) of the stock-guiding passageway between 223224; and said parting-line 225 being interrupted horizontally midway by an interlocking downward projection 229A, Fig. 19,

formed integral with the upper box-half 224; the lower half 223 being correspondingly formed to receive and longitudinally lock 223 with 224; it being understood that such interlocking between 223-229 only extends to the central stock passage-way thru die G as indicated in Fig. 19.

The orifice to said stock passage-way between 223-229 is formed with a wide bell-mouth on the stock-entering side (left toward reel A, Figs. 6, 19) the easier to receive the original van of a coil of stock being introduced thru the machine, so that incidentally die G acts as a guide for the initial van of stock Z in a coil on the supply-reel.

Stock-discharge Associated with the operating cycle of the flying-shear unit U is the cooperating stock discharge mechanism D3 located to the right of the shear unit U, Figs. 1, 1A, 2A; said discharge unit D3 being inter-connected with the shearing mechanism by way of the miter gears 24-45, Figs. 2, 3, 4, 6 and '7; miter-gear 24 being fixed to shaft l! with its hub 24A preferably formed to support the gear MA as shown in Figs, 4, '7; and miter gear 25 being fixed to the end of the long cam shaft 32, Figs. 2, 4, 6; said shaft 32 being locally supported at a point adjacent the mounting of miter-gear 25 by a detachable bearing bracket 26 which is rigidly seated on the ledge 36C of the shear-frame pedestal 39. To shaft 32 is keyed cam 27, as shown in Fig. 15A, to cause discharge of sheared sublength of stock. This cam preferably is pluralized along shaft 32, to provide one cam for each of the plural rocking-levers 28. With the tripping of target K by the van of the parent stock Z and the subsequent power locking of shafts 49fi2 with the continuously rotating fly-wheel bull-gear i of clutch L for a one revolution fabricating cycle, cam-shaft 32 will be rotated and earns 2'! revolved via the miter-gears 24--25 thru a tuned companionate one-revolution stockdischarging cycle.

The zero position of said cam or cams 21 corresponding to the zero positions of trunnions or pins 39 at eight oclock of Fig. 15, is shown in 15A where one of the discharging cams 2'! is shown lying horizontally and in that position supporting one of the rocking-levers 28 mounted on the stock-discharging rock-shaft 29, cam 21 in that position lying ready to lift 28 and lower 96 via pivot-shaft 29; said shaft 29 normally being under a clockwise closing torsion from the helical compression springs 64,

one for each of levers 28, Figs. l5A-18A, to hold them in contact with cams 21. This compression of springs 94 keeps the bottom stock-guide 96 tightly closed upwards against the bottoms of the two combination top-and-side stock-guides 5 9898, Figs. 7-10, 15A, guides 96, 98, 98 forming substantially a box into which stock Z is fed; and bottom stock-guide 96 being suspended from the rock-shaft 29 by the supports 91 to which guide 96 is attached by the stud-bolts 95,

Figs. 8-9.

Between the closed stock-guides 96, 98-98 there is formed a stock-guiding passage 0, Figs. L8, 10 for the stock Z as its successive vans are continuously fed to the target-unit K, Fig. 10, for the pro-gauging of the linear dimension of the fabricated sub-length Zl therefrom and causing tripping of clutch L and the subsequent shearing of ZZl by G-H with subsequent dumping of the freshly severed sub-length ZI by the earns 21 from the box 96, 98, 98.

The springs 64 are attached to the rock-shaft 29 via the pull-down connecting-rods I05, the pivot-pins 206 and the crank-levers I91, Figs.

7, A-18A; springs 64 obtaining their anchorage and actuating purchase from the shaft-like alining-rod I98 thru the medium of the spring-support member I99; the latter being formed to house the spring 64 and to guide the pull-down connecting-rods 595 assisted by the spring-retain- A ing piston-like guide-plugs H9, which also assists the hexagonal nut III to regulate the tension of springs 64, Figs. 15A-18A; said springsupport members I99 being pivotally free on the support-rod I08 and thereon longitudinally positioned between the fixed shaft collars I l2--l I2, Fig. 11.

Hence, when a van of stock Z is fed, Fig. 10, to the target-unit K, to unlatch clutch L from Fig. 22 to Fig. 23 and initiate operation of the flying-shear mechanism U and cam-shaft 32 of the stock-discharge unit D3, the cams 21, Fig. 15A, supporting the rocking-levers 28 are revolved anti-clockwise to rock the shaft 29 and so raise levers 28 against the restraining downward pull of the helical springs 64; all this for the purpose of swinging the bottom stock-guide 99 anti-clockwise away from guides 98-98 as in Figs. 16A, 17A to open the bottom of the stockbox and release the freshly severed sub-length alinement .ZI,.Fig. 16,-fromits confinementin the guide passageway but when the cams 21 have been rotated past their maximum actuating position,- Fig. 17A, and when sub-length ZI has been transverscly discharged from its feedingand shearing .supports 96, 98-98, as shown then' the springs '64 once more are free to exert themselves to rotate shaft 29 clockwise, Fig. 18A, thus returning 98-91 to their positions of rest .as shown in Figs. 15A, 18A; allof this discharging action taking place in a Very short time so that the guide passage 0 between the stock guides 95 and:98--i8is quickly re-formed by the upward movement of 95 to receive the newly formed van of the parent stock Z, Fig. 18, and to guide it to the length-master or target unit K, Fig. 10, for repetition of the .foregoing cycle .of operations.

The skeleton structure of discharge unit D3, Figs. 12A-18A, together with'its association and with the heavier structure ofthe machine proper (including frame Q, ISI-I32 and I44 etc., Fig. l) is maintained mainly thru the longitudinal tubular component member 8!,

Figs.:1-2,-and-its connecting flange 82 which form' the structure 7 the means by which D3 is fixed to .of the machine proper; the uprights N-NI being;suitably spaced along M, Fig. 1A and the leftehand'upright NL'Fig. 1 right, nearest the shear Uzbeing further tied .to the machine structure bythe short tie-memberthFig. 1; while at f .the same time N I .is rigidly spaced from the com panionate uprights N, Fig. 1A, by the tie bar I0 8, Figs. 15A18A,"each'upright N being individually .drift-ikeyedto I538 via 'Ii3II i as depicted in the details of Fig. 11.

While not necessary, it is preferable, as when themachine is under construction, to individually'affix the uprights 'N-NI 'to the tubular-sup- .port 8I, by.-first adjusting said uprightsN-Ni to the desired alinement with the several operating units of the machine proper on center-to-center' spacings of substantially five feet apart in the exemplary machine 'andthen running molten babbitt-in between said tubular support BI and "theopenings BIA, Fig.7, in the assembled upright units N-'NI. This in eiiect casts said up rights NNI solid with the tubular support '8I, forming a relatively substantially rigid structure forthe discharge mechanisms D3 and keeping stock-guiding passage 0, formed by the stock-guides 98, 93-98, in working alinement with the path of the continuously fed stock Z. 'This construction of the stock-discharging mechanism D3 allows (thru the freeing of the bearing-bracket 25, the

, flangeBZ as by the removal of the nuts off the flange-studs 828, Fig. 3) the separation of the stock-discharge mechanism D3 from the frame a of the machine proper so that thesame may the etc.

.ponent-casting of the stru be necessary to replace the whole if some component suffer damage.

' position of K actuated by tie-member 83 and the The top-castings H of N-NI support both the topand-side"stockeguides 9898 with the cap.-

the V upright units suspended combination 7 screws 92 and the inverted channel-formed busbar support 7 be noted that the manner of sup- 7-9. It is to port by II! of the guides 98 -98 does not interv fere with the longitudinal passage of the target: unit K, Figs. 7-9, at any point ofits movement along the inter-locked top surfaces of the guide members Qfi-QB; one of the top-guides 98 being suitably graduated, thruout its length with suitable markings of feet and register in due relation with the pre-gauging the stock-van andthe subsequent point of stock severance by the blades G I-I of unit U.

Target K The supporting body-member I 45 ofunit K,

Fig. 10, is formed with hooks i45AI45A which engage with the overhanging ledgesfiih-QS of inches all of which guides QB, so that unit'K supported by said bodymember I may be horizontally adjusted and guided by ledges 98-39; the graduations at 99A of guideQB-indicatin-g approximately the position a the indicated linear dimenbeing elfected thru the seta sub-length 21 of sion; said clamping screw I46 threadedly mounted in the body-member I and contacting with the graduated surfaceQQA of guide 98'thru a sof t-copperplug i4? Fig.9, which prevents undue marring of said graduated surface 99A of. guide "98 by set-screw bifurcatedly formed at port'the stop I48 which swings on pivot-pin I49, Figs. 10, 21, fixedin the said bifurcated portions 1453 of the body-member I45, Fig. 10. In operation the feeding stock Z strikes the lower end KF of the target and "swings it anti-clockwise to operate the switch to operate the clutch L.

To that side of stop I48 away from the supporting body-member I (to the right Figs.

9=l0) is attached by means such as the rivets I52, Figs. 9-10, the combination trip-,and-contact support member I 5!,Fig. 21,'which is formed with a sub-extending" vertical portion KF thatprojects centrally downwards thru the slot i 7 or channel between guides 53, 93 into thru which stock 2 is fed left to right thru the passage 0 between the guides 96, 98-438, Figs. 10, 19; andto the upturned portion I5IA, Figs.

9-10, is rigidly attached the insulating member I58 via the bolt-element 59 whose fillister head is set suificiently below the surface of 58 to al low the same to be covered 'with some sorter" plastic insulation. such as sealing wax (not shown); this provides complete isolation of the combination trip-and-contact-support member I5I from the copper contact are'fixed to :the insulating bolt-elements I6I, Figs. 8, 10, 13; and the heads of'bolts I fiI are preferably also isolated from IEIA, Fig; 13, by the use of plastic insulation (not shown).

Asthe van of stock Z element I58 by the is fed further'to the,

flag-portion KF of the combination trip-and contact support member I5I to push 'KF anticlockwise out of its way and, in so'doingthe far end I5IA, supporting lEiB-IEI,

terminals of ISO-I56 into contact with the bus The supporting body-member 54 5 of unit K is H153 to straddle and sup-' ,to which unit :K is to be clamped for fabricating V r the path 7 elements I58. which right, it will make contact with the suspended is pivotally raised at I49 to bring 'thetwo bifurcated contact 

